Swivel slide bearing

ABSTRACT

The invention relates to a swivel slide bearing comprising an inner first bearing part ( 31 ) with an outer first bearing surface ( 31   a ) and comprising an outer second bearing part ( 32 ) with an inner second bearing surface ( 32   a ). The outer bearing part ( 32 ) surrounds the inner bearing part ( 31 ), and the outer periphery of the outer bearing part ( 32 ) is provided in the form of a ring having a spherical segment-shaped third bearing surface ( 32   b ), via which it is mounted, whereby being able to move in a manner similar to a ball but in a limited manner, inside a third bearing part ( 33 ) having a spherical segment-shaped inner fourth bearing surface ( 33   a ) that encircles the third bearing surface ( 32   b ). In order to ensure an easy mounting, at least one insertion slot ( 36 ) is provided on one side of the third bearing part ( 33 ), and the second bearing part ( 32 ) until it reaches a position in which the center of curvatures (M) of the third and fourth bearing surface ( 32   b,    33   a ) overlap.

The invention relates to a swivel slide bearing according to thepreamble to claim 1.

With the slide bearing mounting of shafts by means of two rotarybearings having an axial distance from one another, in particular withreciprocating or piston engines or axial piston engines, the followingrequirements arise, among others:

Due to the tolerances, which can scarcely be avoided, it is necessaryfor at least one of the two swivel bearings to have the possibility ofcompensating for the deficient alignment between the swivel bearings. Onthe other hand, it is also a requirement for at least one of the swivelslide bearings to be suitable for providing reliable and long-termbearing support for the drive shaft even with the deflection andflexural movements which occur under full load.

With known piston engines or axial piston engines, conventional rollingbearings are used which are capable of accommodating radial forces and,if required, also axial forces. It is true that these bearings are stillfunctional even in the event of deficient alignment of the bearings ordeflection of the shaft, but the risk of overloading pertains, which inturn leads to increased wear, increased heating, and reduction of theservice life.

A swivel slide bearing of the type referred to in the preamble isdescribed and represented in DE 43 36 915 A1 without indication of anyspecific area of application. With this generic design, the fitting andremoval of the swivel slide bearing is problematic. Accordingly, in thatcase the housing-side bearing body is designed in several parts,although this renders installation more difficult.

The object of the invention is to provide a swivel slide bearing of thetype referred to in the preamble which can be fitted and removed in asimple manner.

This object is achieved by the features of claim 1. Advantageous furtherembodiments of the invention are described in the Sub-Claims.

With the embodiment according to the invention, the third bearing parthas on one side at least one entry guide slot, in which the secondbearing part can be introduced in an angle-rotated position as far asinto a position in which the curvature mid-points of the bearingsurfaces essentially cover one another. In this position, the secondbearing part can be rotated into its function position, in which itsmid-axis is essentially in alignment with the mid-axis of the thirdbearing part.

The invention is based on the finding that, when the curvaturemid-points lie in one and the same point, the bearing parts can rotaterelative to one another about the curvature mid-point, because thespherical segment-shaped bearing surfaces are located in a suitableposition in relation to one another to allow for rotation into anapproximately co-axial position during mounting, and rotating back intoa transverse position corresponding to the entry guide slot. In thissituation the invention is further based on the finding that, when theaxial width of the first bearing part is smaller than the peripheraldiameter of the spherical segment-shaped bearing surface of the outerbearing part and the width of the entry guide slot is likewise smallerthan the peripheral diameter despite the presence of the entry guideslot, sufficiently large surface sections of the sphericalsegment-shaped bearing surface remain to allow, with the first bearingpart in the mounted position, for the outer bearing part to engage inpositive fit behind the inner bearing part on this side, and thereby foradequate axial as well as radial support to be guaranteed.

If it is intended that the spherical segment-shaped bearing surfacesshould exclusively form support surfaces, and the bearing surfacesbetween the first and the second bearing part should fulfil the slidefunction, it is advantageous for the second bearing part and the thirdbearing part to be secured against rotation in respect of one another.Securing against rotation can be provided by means of a pin passedthrough the dividing surfaces between the bearing surfaces in the formof a spherical segment, which is preferably located in a radial hole ofthe second bearing part and is secured in this, e.g. by means of a pressfit. The pin can, however, also be secured in a hole in the thirdbearing part. In the other bearing part in each case, preferably, alongitudinal hole is provided for the pin, extending in the axial planeof this bearing part, so that in the axial mid-plane limited relativepivotal movements can be carried out between the second and thirdbearing part, in order, during fitting, for the pin to be introducedinto the longitudinal hole or to be guided out of it during disassembly.

In addition to this, the inner bearing surface in the shape of aspherical segment on the third bearing part and the outer ring-shapedbearing surface on the first bearing part can in each case be designedto form one function unit, for example on a shaft or a housing, of theengine concerned, or in an additional bearing sleeve, which can havespecial bearing function features in a simple and economical manner. Forthis purpose it can, for example, consist of a special material, whichis well-suited for a bearing, or be replaceable as a part subject towear, so that the service life of the other bearing parts can beextended by the replacement of the additional bearing sleeve in eachcase.

Features are contained in the additional Sub-Claims which allow for thedesign of the swivel slide bearing in relation to the drive shaft as aloose or fixed bearing, which lead to the improvement of the servicelife of the swivel slide bearing due to effectively functioninglubrication features, and also lead to a simple, small design, which canbe manufactured economically.

Advantageous embodiments of the swivel slide bearing according to theinvention are described in greater detail hereinafter on the basis ofthe drawings. These show:

FIG. 1 An axial piston engine in an axial view;

FIG. 2 The detail characterised in FIG. 1 by II, with a swivel slidebearing according to the invention, in an enlarged sectionalrepresentation;

FIG. 3 The part section III-III in FIG. 2;

FIG. 4 A swivel slide bearing according to the invention, in aperspective representation as a modular part, partially in section;

FIG. 5 The swivel slide bearing according to FIG. 4, in another functionposition;

FIG. 6 The swivel slide bearing in a pre-mounting position;

FIG. 7 An outer bearing part of the swivel slide bearing in an axialsection;

FIG. 8 The swivel slide bearing in a modified embodiment, in an axialsection;

FIG. 9 The swivel slide bearing in a further modified embodiment, in anaxial section;

FIG. 10 The swivel slide bearing in a further modified embodiment, in anaxial section;

FIG. 11 A swivel guide bearing according to the invention in a modifiedembodiment, in an axial sectional representation;

FIG. 12 A second and a third bearing part of the swivel slide bearing ina perspective representation.

FIG. 13 A section of the swivel slide bearing in a front face view.

The piston engine represented in FIG. 1, arranged by way of example anddesignated in its totality as 1, has a housing 2, in the interior space3 of which are arranged next to each other an oblique disk 4 and acylindrical drum 5. Arranged in the cylindrical drum 5, distributedaround the circumference, are piston holes 6, which in the presentembodiment of an axial piston engine extend essentially parallel to amid-axis 7 of the cylindrical drum 5 and are open on the face side 5a ofthe cylindrical drum 5 which is turned towards the oblique disk 4. Guidebushings 8 are securely located in the bushing holes 6, preferablypressed into place.

Mounted in an essentially axial displaceable manner in the guidebushings 8 are pistons 9, preferably cylindrical, which with theirpiston heads delimit working chambers 11 in the cylindrical drum 5 inthe direction towards the oblique disk 4. The foot ends of the pistons9, turned towards the oblique disk 4, are supported in each case by ajoint 12 at the oblique disk 4, whereby slide shoes 13 may be present,between which and the foot ends the joints 12 are arranged, preferablydesigned as ball joints with a ball head and a ball recess.

The cylindrical drum 5 is located with its face side turned away fromthe oblique disk 4 in contact with a control disk 14, in which at leasttwo control apertures 15 are arranged in the form of kidney-shapedthrough holes, which form sections of a feed line 16 and a departureline 17, only indicated, which extend through an adjacent housing wall18, to which the control disk 14 is held. The cylindrical drum 5 isarranged on a drive shaft 19, which is rotatably mounted in the housing2 and of which the axis of rotation 21 runs co-axially to the mid-axis 7of the cylindrical drum 5.

With the present embodiment, the housing 2 is formed from a pot-shapedhousing part 2 a and a cover or connection part 2 d forming the housingwall 18, which is in contact at the free edge of the circumferentialwall 2 c, and is screwed to this by means of screws 22, represented byindication only. In order to provide a connection with the feed anddeparture lines 16, 17, line connections 16 a, 17 a are provided at theconnection part 2 d. The drive shaft 19, which passes through thecylindrical drum 5 in a bearing hole, is rotatably mounted and sealed inbearing cut-outs of the housing base 2 b and of the cover 2 d by meansof suitable bearings 25, 25 a, whereby it passes axially through thehousing base 2 b and stands clear of the housing base 2 b by means of adrive journal 19 a.

With the embodiment of the piston engine 1 as an oblique disk engine,the cylindrical drum 5 is arranged in a torsionally-resistant manner onthe drive shaft 19 by means of a rotary drive connection 26, such as atoothed coupling, whereby the shaft passes through the oblique disk 4,arranged fixed to the housing base 2 or formed in it, in a through hole27. In the present embodiment, the cylinder drum 5 rotates in functionaloperation relative to the oblique disk 4, whereby the pistons 9 aredisplaced longitudinally in the direction of the working chambers 11 andback again.

In the embodiment, the rear bearing 25 a, mounted in the housing wall 18or in the connection part 2 d, is a swivel slide bearing 25 b, which iscombined with a spherically movable swivel slide bearing 25 c, so thatit is in a position to mount the drive shaft 19 in a rotatable mannerand, in addition, to compensate for deficiencies in the alignment of thebearings 25, 25 a, and/or flexural movements of the drive shaft 19,which arise in functional operation. As a result of this, tiltingmovements in the swivel slide bearing 25 b are avoided or reduced, whichimproves the slide function, reduces the friction and heat in the swivelslide bearing 25 d, and increases the service life.

The spherically-movable swivel slide bearing 25 c, combined in themanner previously described, has an inner first bearing part 31 with anouter first bearing surface 31 a, with which it is rotatably mounted inan outer second bearing part 32 with an inner second bearing surface 32a, with sliding play. As a result of this, the outer second bearing part32 surrounds the inner first bearing part 31, whereby the outer secondbearing part 32 is formed at least at its outer circumference as a ringwith a spherical area-shaped outer third bearing surface 32 b, withwhich it is capable of limited spherical movement; that is to say, itcan be tilted on all sides in relation to the axis of rotation 21,mounted in a third bearing part 33 with an inner fourth bearing surface33 a formed at least partially in a corresponding spherical segmentshape.

In the embodiment shown, the second bearing part 32 and the thirdbearing part 33 are formed as rings, which, for example, may have anequal axial width b. In the embodiment, the first bearing part 31 isdesigned wider than the second and third bearing parts 32, 33,overlapping these, for example on both sides.

In addition to this, in the embodiment shown, the first bearing part 31is formed by a bearing bushing 31 b, preferably of hollow cylindricalcross-section, which is arranged in a torsionally-resistant manner on abearing journal 19 a of the drive shaft 19, located on the bearingjournal 19 a by means of a press fit, for example.

The third bearing part 33 is preferably likewise a bearing sleeve 33 b,which is located in a torsionally-resistant manner in or on thecomponent which supports it, in this case on the cover or connectionpart 2 d. For this purpose a bearing hole 34 is provided therein for theround third bearing part 33, preferably with a shoulder surface 34 a,formed by an inner step, which delimits the third bearing part 33axially outwards. In the embodiment shown, the bearing hole 34 extendsinwards over the dividing surface 2 e between the connection part 2 dand the control disk 14 into the latter, a shoulder surface 34 bpreferably also being arranged here, which delimits the outer bearingpart 33 inwards, as a result of which it is positioned axially inpositive fit. With this embodiment, the bearing bushing 33 b forms acentering journal for centering the control disk 14.

The embodiments according to FIGS. 1 to 9 and 11 to 13 are arranged fora rotational movement between the first and the second bearing part 31,32 and for a spherical movement or tilting movement between the secondand third bearing part 32, 33. In order to prevent a rotational movementabout the axis of rotation 21 between the second and the third bearingpart 32, 33, a rotation blocking device 35 with a journal connection isprovided with a positive fit between the second and the third bearingpart 32, 33. The journal connection comprises a blocking journal 35 b,held at a distance from one of these two bearing parts 32, 33, andengaging into a longitudinal hole 35 a of the other bearing part 32, 33,the longitudinal hole 35 a extending along the axis of rotation 21. Inaddition, the longitudinal hole 35 a and the blocking journal 35 b arelocated in the radial plane Er of the bearing part 32, 33 concerned,containing the curvature mid-point M. As a consequence, a rotationalmovement between the bearing parts 32, 33 is blocked, although a limitedtilting movement on all sides is possible, which allows for thecompensation measures previously described.

The blocking journal 35 b can be formed by a circular pin 35 c, which islocated securely in a hole in one of the bearing parts 32, 33, e.g. ispressed into place, and engages with its projecting, e.g. thickened,head into the longitudinal hole 35 a of the other bearing part 32, 33with a degree of movement play. In the embodiment shown, the pin hole isarranged in the second bearing part 32 and the longitudinal hole 35 a isarranged in the third bearing part 33.

The blocking journal 35 b is preferably arranged in the longitudinalmid-plane E intersecting symmetrically the control openings 15, or inthe longitudinal mid-plane E1 extending at a right angle thereto. Thereason for this is that the sum of the piston forces exerts a resultanttransverse force, taking effect in the longitudinal mid-plane E, on thedrive shaft 19, which can incur a slight flexing of the drive shaft 19in the form of torque, which is compensated for by a tilting movement inthe longitudinal mid-plane E. This tilting movement can be carried outby the spherically-movable bearing 25 c in all transverse directionswith no problem, and in particular in cases in which the longitudinalhole 35 a extends in the longitudinal mid-plane E, or also if it islocated in the longitudinal mid-plane E1. In this position a tiltingmovement as described heretofore takes place about the mid-axis of theblocking journal 35 b extending transversely.

The third bearing part 33 has on one side an axial entry guide slot 36,which is designed in respect of its transverse dimensions A, B, and inits cross-sectional form, to be larger than the axial cross-sectionalsize and form of the second bearing part 32, so that the latter can beintroduced into the guide slot 36 in an angle-rotated position, e.g. ina position rotated about some 90°. The axial length of the guide slot 36is of sufficient dimensions for the second bearing part 32 to be able toslide in it into an intermediate position in accordance with FIG. 5, inwhich the curvature mid-points of the third and fourth bearing surfaces32 a, 33 a lie in the common curvature mid-point M and thereforeoverlap. In this position, the second bearing part 32 can be rotatedinto its end position, in which its longitudinal mid-axis isapproximately flush with the longitudinal mid-axis of the third bearingpart 33. In this end position, rotated back, the second bearing part 32is positioned axially in positive fit in the third bearing part 33through the rear section of the spherical segment-shaped fourth bearingsurface 33 a.

In the embodiment shown, two guide slots 36 are arranged diametricallyopposite and mirror-symmetrically to one another, so that the secondbearing part 32 can be introduced centrally into the third bearing part33. The rounded base surfaces 36a of the guide slots 36, locatedopposite one another, preferably corresponding in cross-section to thecross-section D of the second bearing part 32, are preferably formedtangentially to the spherical segment-shaped fourth bearing surface 33a, so that they run out centrally in the third bearing part 33 and passover into the spherical segment-shaped fourth bearing surface 33 a. Thishas the particular advantage that the introduced second bearing part 32forms stops for the inward thrust movement of the second bearing part32, at the sections of the spherical segment-shaped fourth bearingsurface 33 a located axially opposite the entry guide slots 36, andspecifically in the intermediate position in which the curvaturemid-points cover one another and the second bearing part 32 isrotatable. This ensures a simple and handling-friendly mounting. Thesecond bearing part 32 needs only to be moved as far as an insertionthrust stop and then rotated.

With the embodiment shown, the width B of the at least one entry guideslot 36 is about ½ to ⅓ of the diameter D of the second bearing part 32.With this dimension, sufficiently large sections of the sphericalsegment-shaped fourth bearing surface 33 a are present next to the atleast one guide slot 36 to guarantee the positive-fit rear engagement inthis axial direction.

To secure the third bearing part 33 against rotation in the housing wall18, a press-fit can be used between the circumference of the thirdbearing part 33 and the wall of the bearing hole 34. With the embodimentshown according to FIG. 8, in which the same or comparable parts areprovided with the same reference numbers, a positive-fit effect rotationblocking device 37 in the form of a journal connection is provided inthe housing wall 18 or in the connection part 2 d, which passes throughthe third bearing part 33 and engages into a longitudinal hole 37 a inthe housing wall 18 which corresponds essentially to the longitudinalhole 35 a. In this arrangement, not only the second bearing part 32 butalso the third bearing part 33 is positioned in positive fit at thehousing wall 18, secured against rotation in the circumferentialdirection.

The mounting of the second bearing part 32 and the introduction of theblocking journal 35 b into the longitudinal hole 35 a is effected insuch a way that the second bearing part 32 is introduced in a positionin which it is rotated with the blocking journal 35 b in relation to thelongitudinal hole 35 a (FIG. 6) so far that the blocking journal 35 bcan be introduced into the guide slot 36. When the blocking journal 35 bis located in the area of the longitudinal hole 35 a, the second bearingpart 32 is rotated back, the blocking journal 35 b entering into thelongitudinal hole 35 a. This is possible with no problem due to thespherical segment form of the second bearing part 32.

In the embodiment according to FIG. 8 too, with the appropriatedimensions it is possible for the lengthened blocking journal 35 b to beintroduced into the longitudinal holes 35 a, 37 a in such a way that thesecond bearing part 33 [sic] is introduced in a torsionally-resistantmanner and is then rotated back, as has already been described for theembodiment according to FIGS. 2 to 6. It is also possible, however, forthe longitudinal hole 37 a to run out to the side from which the thirdbearing part 33 can be pushed into the bearing hole 34. With thisembodiment, the third bearing part 33, with the second bearing part 32mounted in it, can be pushed into the bearing hole 34, whereby theblocking journal 35 b can also be introduced into the longitudinal hole37 a. With the embodiment according to FIG. 8, this is possible from theinner side, because the longitudinal hole 37 a runs out to the dividingsurface 2e between the housing wall 18 and the control disk 14, and thisspherically-movable swivel slide bearing 25 c can be mounted before thefitting of the control disk to the housing wall 18 or before the fittingof the housing wall 18 to the control disk 14.

With the embodiment according to FIG. 9, in which the same or comparableparts are provided with the same reference numbers, another arrangementof the rotation blocking device 37 is provided, whereby the rotationblocking device 35 can be designed in accordance with FIG. 8. Accordingto FIG. 9, the rotation blocking device 37 is likewise formed by ajournal connection, although this is not transverse in relation to theaxis of rotation 21 but axially parallel and formed by a blocking pin 37c, which is arranged in the area of the step surface and engages inholes located opposite one another in the housing wall 18 and in thethird bearing part 33.

The embodiment according to FIG. 10, in which the same or comparableparts are likewise provided with the same reference numbers, makes itclear that it does not require a separate third bearing part 33 if theinner fourth bearing surface 33 a and the at least one entry guide slot36 are formed directly at the housing wall 18 or the connection part 2d. With this embodiment too, blocking devices can be provided in thesense of FIGS. 8 or 9, whereby the longitudinal hole 35 a can bearranged in the housing wall 18 (not shown).

With the present piston engine or axial piston engine 1, hydraulicfluid, e.g. hydraulic oil, is located in the interior space 3, which infunction operation can be used for the lubrication of the bearingsurfaces 31 a, 32 a, and preferably also of the bearing surfaces 32 b,33 a. Particularly well-suited as lubricating fluid is a lubricatingfluid containing water, which contains about 50% water and about 50%glycol, and is known in the specialist sector under the designation HFC.

In order to ensure the accessibility of the lubricating fluid located inthe interior space 3, and in particular to the swivel slide bearing 25b, it is advantageous for an axial passage 14 a to be provided betweenthe control disk 14 and the drive shaft 19, which guarantees access forthe lubricant fluid at least to the swivel slide bearing 25 b. In theembodiment shown, the control disk 14 has a passage hole which surroundsthe drive shaft 19 with an annular space interval. The diameter D1 ofthe through hole is preferably greater than the external diameter of thefirst bearing part 31 or of the bearing bushing 31 b, with the resultthat an annular access to the bearing surfaces 31 a, 33 a, andpreferably also to the bearing surfaces 32 b, 33 a, is guaranteed.

To further improve the lubrication system, it is advantageous to makeprovision in at least one of the bearing surfaces 33 a, 32 a, in thiscase in the inner second bearing surface 32 a, for one or morelubrication grooves 38 distributed around the circumference, which canextend axially or obliquely or helicoidally, as shown in FIGS. 2 to 7.With an oblique or helicoidal arrangement of the at least onelubrication groove 38, a carrying area B1 is located on each axial sideof the second bearing part 32, which is delimited by the edge of thelubrication groove 38 belonging to it and by a bearing surface line 39extending axially.

With the previously described embodiments, the swivel slide bearing 25 cis what is referred to as a loose bearing in relation to the drive shaft19, i.e. there is no mutual axial support between the drive shaft 19 andthe first bearing part 31 arranged secured on this and the secondbearing part 32. By contrast, this axial support is provided between thethird bearing part 33 and the housing 2 or, respectively, the housingwall 18 accommodating the swivel slide bearing 25 b. There are alsosituations, however, in which axial support is desirable between thefirst and the second bearing parts 31, 32 in at least one axialdirection. This can be achieved in that the second bearing part 32 isdelimited on one or both sides in each case by a shoulder or bearingsurface, which is arranged at the drive shaft 19 or at a fitted partthereof. A swivel slide bearing of this kind, designed in at least oneaxial direction as a fixed bearing, can be formed with two bearing parts31, 32 as a swivel slide bearing 25 b, or with the second and thirdbearing parts 32, 33 as a tiltable swivel slide bearing 25 c, andtherefore can absorb axial forces in one or in both axial directions.

With the embodiment according to FIG. 11, in which the same orcomparable parts are provided with the same reference numbers, theswivel slide bearing 25 c is arranged as a fixed bearing in the area ofthe housing 2, in this case in the housing base 2 b, and taking effectin both axial directions, whereby it can form the bearing 25 a arrangedin the connection part 2 d or, preferably, the bearing 25 arranged inthe housing base 2 b, as FIG. 11 shows. The second bearing part 32 isdelimited on both face sides by a support flange 42 a, 42 b withmovement play, which is fixed axially at the drive shaft 19 or at thefirst bearing part 31. With the embodiment shown, a support flange, inthis case the outer support flange 42 a, is connected as a single pieceto the first bearing part 31, these parts forming an angular ring body,and the inner support flange 42 b having a coaxial hole 43, theperipheral hole with which it is located on the drive shaft 19, havingslight movement play. On the side turned away from the swivel slidebearing 25 c, the support flange 42 b can be supported axially by adrive shaft shoulder 44, which is formed in the embodiment shown by aspring-loaded ring, located in an annular groove in the drive shaft 19.The first bearing part 31 preferably extends as far as the surface,turned towards it, of the second support flange 42 b, and in the otheraxial direction, in this case outwards, it is axially supported by adrive shaft shoulder 45, which, as a single-piece flange ring, can belocated at a distance from the drive shaft 19.

For the purpose of lubrication, provision is made in each case for oneor more lubrication grooves 46 a, 46 b in the shoulder surfaces orsliding surfaces 42 c of the support flange 42 a, 42 b (not shown) or inthe face surfaces 32 c of the second bearing part 32, arrangeddistributed on the circumference and running from the inside outwards,which are in connection radially inwards with a lubricant supply lineand in connection radially outwards with a lubricant departure line andare therefore part of a lubricant circuit 47, through which a lubricant,e.g. hydraulic oil, flows when the piston engine is in operation. Nospecial lubricant pump is required in order to maintain the flow in thelubricant circuit 47. The lubricant which is in the lubrication grooves46 a, 46 b during operation creates the flow in the circuit 47automatically, due to the centrifugal force which takes effect on thelubricant. The lubricant circuit 47 may, for example, be connected tothe interior space 3 of the housing 2.

An additional conveying effect on the lubricant can be achieved if thelubrication grooves 46 a, 46 b are inclined at an angle, and inparticular if the lubrication grooves 46 a on the one side and thelubrication grooves 46 b on the other side are inclined in oppositedirections to one another. It is possible for the lubrication grooves 46a (not shown) located in the rotating bearing part, in this case in thesupport flanges 42 a, 42 b, to be inclined opposed to the direction ofrotation of the rotating bearing part, or the lubrication grooves 46 a,46 b, located in the non-rotating bearing part, in this case the secondbearing part 31 [sic], to be inclined in the direction of rotation. Theinclination can also be spiral shaped. With these embodiments a forceddelivery effect is exerted on the lubricant by the contact between thebearing surfaces, in this case the support flanges 42 a, 42 b, and thelubricant columns located in the lubricant grooves 46 a, 46 b. With theembodiment shown, in which the lubrication grooves 46 a, 46 b arearranged in the non-rotating second bearing part 32, the forced deliveryeffect is produced by the contact created by the bearing surfaces 42 cof the rotating first bearing part 31, formed by the support flanges 42a, 42 b.

With the embodiment shown, lubrication grooves 46 a, 46 b, arranged onboth sides of the second bearing part 32 and pertaining to one another,are connected to the at least one lubrication groove 38 which can belocated in the outer casing surface of the first bearing part 31 or inthe inner casing surface of the second bearing part 32, and in thissituation can be extended axially, such as is shown, for example, inFIGS. 4 and 5, or can extend obliquely, as is shown, for example, inFIG. 7. With an oblique course of the lubrication groove 38, the forceddelivery effect is also produced in the area of the lubrication groove38. The delivery effect is created by the contact which the bearingsurface adjacent to the lubricant in the at least one lubrication groove38 exerts on the lubricant. In this situation, the lubrication grooves46 a, 46 b connected to one another by the straight lubrication groove38, or the lubrication grooves 46 a, 46 b connected to one another by anoblique lubrication groove 38, and also the oblique lubrication groove38, are aligned in such a way that the delivery effect takes effect insequentially-following directions and result in a continuous deliveryeffect in the lubrication groove sections 46 b, 38, 46 a. In operation,the lubricant then enters at the radially outer end of the lubricationgroove or lubrication grooves on the one side, and emerges at theradially outer end of the lubrication groove or lubrication grooves onthe other side. The axial course of the delivery effect or the deliverydirection outwards or inwards is dependent on the direction of rotationof the drive shaft 19 or of the first bearing part 31.

In the embodiment shown, the lubricant circuit 47 is formed by theinside lubrication grooves 46 b being open radially outwards to theinterior space 3. The outside lubrication grooves 46 a are likewise openradially outwards, and they can likewise be connected to the interiorspace 3 by means of a lubricant channel, not shown.

FIG. 11 shows an embodiment in which a swivel bearing lubricationarrangement for an inherently-known pivotable oblique disk 4 isadditionally incorporated into the lubricant circuit 47. In thisembodiment, the lubricant grooves 46 a open radially outwards into apreferably ring-shaped gap, or a lubricant channel section 47 a, fromwhich a lubricant channel 47 b leads further in the housing base 2 b,extends, for example, in an angular manner to the slide bearing surface48 of a swivel bearing 49 for the oblique disk 4 mounted in a pivotablemanner in this embodiment, and in this situation passes through abearing shell 51 of the swivel bearing 49. The swivel bearing 49,arranged on the other side of the piston engine 1 in relation to theaxis of rotation 7 of the drive shaft 19, can be connected in a similarmanner to the lubricant circuit 47, which for the sake of simplicity isnot shown.

In the embodiment shown, the directions of flow of the circuit flow inthe area of the swivel slide bearing 25 c, going outwards from theopenings of the lubrication channels 46 b, are initially directedradially inwards, then axially outwards, and then radially outwards; seeS1, S2, S3.

FIG. 13 shows the lubrication grooves 46 a, 46 b, inclined opposed toone another, on both sides of the second bearing part 32.

In the embodiment according to FIG. 12, an axially-effective element 37for securing against rotation is formed in that one or more segments 37d of the ring-shaped body of the third bearing part 33, for example twosegments located opposite one another, project axially, engage inpositioning cut-outs, arranged directly or indirectly at the housing 2or housing base 2 b, into which they engage, or in one or morepositioning journals, engage into the at least one cut-out 37 e presentbetween two segments, for the purpose of interacting in such a way as toprovide torsional resistance by positive fit.

In the embodiment shown, the swivel slide bearing 25 c is located withits third bearing part 33 in a bearing hole 61, which has on the innerside a stop shoulder element 62 for the third bearing part 33 and isextended outwards in stages, whereby in the larger hole stage 63 aclosure ring 64 with a ring seal 65 for the drive shaft 19 is insertedand secured axially by means of a securing ring 66.

1-17. (canceled)
 18. A piston engine, with a housing, in which a driveshaft is mounted such as to rotate by means of a swivel slide bearing,which has an inner first bearing part with an outer first bearingsurface and an outer second bearing part with an inner second bearingsurface, whereby the inner first bearing part is arranged in atorsionally-resistant manner on the drive shaft and the outer bearingpart is designed as one piece and surrounds the inner bearing part withslide play, whereby the outer bearing part is formed at its outercircumference as a ring with a spherical segment-shaped third bearingsurface, with which it is mounted with limited spherical movement in athird bearing part with a spherical segment-shaped inner fourth bearingsurface, which surrounds the third bearing surface, whereby on one sideof the third bearing part at least one entry guide slot is arranged,into which the second bearing part can be introduced in an angle-rotatedposition as far as into a position into the third bearing, in which thecurvature mid-points (M) of the third and fourth bearing surfacesessentially cover one another, and whereby a rotation blocking device isarranged between the second and third bearing parts.
 19. The pistonengine according to claim 18, wherein the second bearing part issupported axially on one or both sides in each case by a support flange,which is supported at the first bearing part or at a component mountingthe first bearing part in the axial direction turned away from thesecond bearing part.
 20. The piston engine according to claim 18,wherein two entry guide slots are arranged opposite one another.
 21. Thepiston engine according to claim 20, wherein the base surfaces of theentry guide slots run out tangentially into the spherical segment-shapedfourth bearing surface.
 22. The piston engine according to claim 18,wherein the width (B) of the entry guide slot amounts to some ⅓ to ½ ofthe diameter (D) of the second bearing part, and the width (b) of thesecond bearing part, at least in respect of a movement play, is smallerthan the width (B) of the entry guide slot.
 23. The piston engineaccording to claim 18, wherein the rotation blocking device is formed bya journal connection between the second and third bearing part and ablocking journal secured to a bearing part with axial movement playengages into a recess in the other bearing part, formed for preferenceby an axial longitudinal hole.
 24. The piston engine according to claim18, wherein the third bearing part is a busing-shaped bearing part,which locates in a bearing hole of an additional bearing part.
 25. Thepiston engine according to claim 24, wherein the additional bearing partis formed by a connection part of a piston engine, in particular of anaxial piston engine.
 26. The piston engine according to claim 25,wherein the bushing-shaped bearing part is delimited on the inside by acontrol disk, which is arranged on the inner side of the connectionpart.
 27. The piston engine according to claim 26, wherein the controldisk is arranged on the inner side of the connection part, whereby anaxial passage for a lubricant fluid is provided in the control disk orbetween the control disk and a drive shaft carrying the first bearingpart.
 28. The piston engine according to claim 18, wherein one or morelubrication grooves are arranged in the bearing surface of the first orsecond bearing part, which are arranged axially or obliquely, and forpreference run out laterally at both ends.
 29. The piston engineaccording to claim 19, wherein in each case one or more lubricationgrooves are provided for or are present in the sliding surfaces of thesecond bearing part and/or of the at least one support flange.
 30. Thepiston engine according to claim 29, wherein the at least onelubrication groove is arranged radially or inclined at an angle inrelation to the circumferential direction.
 31. The piston engineaccording to claim 30, wherein the lubrication grooves located betweenthe second bearing part and the support flanges are inclined on one sidein one circumferential direction, and on the other side in the othercircumferential direction.
 32. The piston engine according to claim 29,wherein the lubrication grooves are connected to one another and form apart of a flow circuit.
 33. The piston engine according claim 29,wherein the lubrication grooves are arranged in the sliding surfaces ofthe second bearing part.
 34. A swivel slide bearing, with a housing, inwhich a drive shaft is mounted such as to rotate by means of a swivelslide bearing, which has an inner first bearing part with an outer firstbearing surface and an outer second bearing part with an inner secondbearing surface, whereby the inner first bearing is arranged in atorsionally-resistant manner on the five shaft and the outer bearingpart is designed as one piece and surrounds the inner bearing part withslide play, whereby the outer bearing part is formed at its outercircumference as a ring with a spherical segment-shaped third bearingsurface, with which it is mounted with limited spherical movement in athird bearing part with a spherical segment-shaped inner fourth bearingsurface, which surrounds the third bearing surface, whereby on one sideof the third bearing part at least one entry guide slot is arranged,into which the second bearing part can be introduced in anangle-rotated, in which the curvature mid-points (M) of the third andfourth bearing surfaces essentially cover one another, whereby arotation blocking device is arranged between the second and thirdbearing parts, and whereby the second bearing part is supported axiallyon one or both sides in each case by a support flange, which issupported at the first bearing part or at a component mounting the firstbearing part in the axial direction turned away from the second bearingpart.
 35. The swivel slide bearing according to claim 34, wherein twoentry guide slots are arranged opposite one another.
 36. The swivelslide bearing according to claim 35, wherein the base surfaces of theentry guide slots run out tangentially into the spherical segment-shapedfourth bearing surface.
 37. The swivel slide bearing according to claim34, wherein the width (B) of the entry guide slot amounts to some ⅓ to ½of the diameter (D) of the second bearing part, and the width (b) of thesecond bearing part, at least in respect of a movement play, is smallerthan the width (B) of the entry guide slot.
 38. The swivel slide bearingaccording to claim 34, wherein the rotation blocking device is formed bya journal connection between the second and third bearing part and ablocking journal secured to a bearing part with axial movement playengages into a recess in the other bearing part, formed for preferenceby an axial-longitudinal hole.
 39. The swivel slide bearing according toclaim 34, wherein that the third bearing part is a busing-shaped bearingpart, which locates in a bearing hole of an additional bearing part. 40.The swivel slide bearing according to claim 39, wherein the additionalbearing part is formed by a connection part of a piston engine, inparticular of a axial piston engine.
 41. The swivel slide bearingaccording to claim 40, wherein the bushing-shaped bearing part isdelimited on the inside by a control disk, which is arranged on theinner side of the connection part.
 42. The swivel slide bearingaccording to claim 41, wherein the control disk is arranged on the innerside of the connection part, whereby an axial passage for a lubricantfluid is provided in the control disk or between the control disk and adrive shaft carrying the first bearing part.
 43. The swivel slidebearing according to claim 34, wherein one or more lubrication groovesare arranged in the bearing surface of the first or second bearing part,which are arranged axially or obliquely, and for preference run outlaterally at both ends.
 44. The swivel slide bearing according to Clam34, wherein in each case one or more lubrication grooves are providedfor or are present in the sliding surfaces of the second bearing part(32) and/or of the at least one support flange.
 45. The swivel slidebearing according to claim 44, wherein the at least one lubricationgroove is arranged radially or included at an angle in relation to thecircumferential direction.
 46. The swivel slide bearing according toclaim 45, wherein the lubrication grooves located between the secondbearing part and the support flanges are included on one side in onecircumferential direction, and on the other side in the othercircumferential direction.
 47. The swivel slide bearing according toclaim 44, wherein the lubrication grooves are connected to one anotherand form a part of a flow circuit.
 48. The swivel slide bearingaccording to claim 44, wherein the lubrication grooves are arranged inthe sliding surfaces of the second bearing part.